WO2020035188A1 - Segment racleur d'huile en trois parties - Google Patents

Segment racleur d'huile en trois parties Download PDF

Info

Publication number
WO2020035188A1
WO2020035188A1 PCT/EP2019/063852 EP2019063852W WO2020035188A1 WO 2020035188 A1 WO2020035188 A1 WO 2020035188A1 EP 2019063852 W EP2019063852 W EP 2019063852W WO 2020035188 A1 WO2020035188 A1 WO 2020035188A1
Authority
WO
WIPO (PCT)
Prior art keywords
ring
curvature
scraper ring
radius
flank
Prior art date
Application number
PCT/EP2019/063852
Other languages
German (de)
English (en)
Inventor
Florian Böhnke
Richard Mittler
Thomas Bastuck
Dirk BÄRENREUTER
Original Assignee
Federal-Mogul Burscheid Gmbh
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Federal-Mogul Burscheid Gmbh filed Critical Federal-Mogul Burscheid Gmbh
Priority to US17/268,140 priority Critical patent/US11719340B2/en
Priority to CN201980053118.1A priority patent/CN112654807B/zh
Priority to EP19727387.3A priority patent/EP3797233B1/fr
Publication of WO2020035188A1 publication Critical patent/WO2020035188A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J9/00—Piston-rings, e.g. non-metallic piston-rings, seats therefor; Ring sealings of similar construction
    • F16J9/06—Piston-rings, e.g. non-metallic piston-rings, seats therefor; Ring sealings of similar construction using separate springs or elastic elements expanding the rings; Springs therefor ; Expansion by wedging
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J9/00—Piston-rings, e.g. non-metallic piston-rings, seats therefor; Ring sealings of similar construction
    • F16J9/12—Details
    • F16J9/20—Rings with special cross-section; Oil-scraping rings
    • F16J9/206—One-piece oil-scraping rings

Definitions

  • Oil scraper rings have been known for a long time, with different designs being used. For example, one-piece oil scraper rings with two scraper bars and
  • Oil scraper rings are often used together with expander springs in order to achieve the most uniform possible contact force over the entire circumference and thus the most uniform possible scraper effect.
  • expander springs There are also so-called three-part
  • Oil scraper rings are known, in which two essentially disc-shaped or flat scraper rings or rails are held apart by a spring in the axial direction in order to be pressed outward in the radial direction.
  • the present invention provides a three part oil control ring having the features of claim 1. Advantageous designs are described in the dependent claims.
  • the wiper rings each comprise an annular body with an upper flank, a lower flank of an inner ring surface and an outer ring surface.
  • Scraper ring flank should be on a piston ring groove flank or on a spring three-part oil control ring in each case in the axial direction.
  • the scraper ring flank should abut a piston ring groove flank or a spring of a three-part oil scraper ring in the axial direction.
  • the inner surface of the ring is intended to be attached to a spring or an expander of a three-part oil scraper ring
  • the outer ring surface has an outer ring contour in a section in the axial direction, which is to run through the axis of rotational symmetry.
  • the annular body has a height H in the axial direction, which corresponds to the greatest distance in the axial direction from the upper flank surface to the lower flank surface.
  • the outer ring surface forms a running surface, the outer ring contour one
  • Radius of curvature R which is a factor of between 1.5 and 6 times, preferably between 3 and 5 times and more preferably between 3.5 and 4.5 times smaller than the height H of the lower or upper scraper ring.
  • the ring bodies of the upper and lower scraper rings each also include a ring joint.
  • the upper and the lower scraper ring are characterized in particular in that they have a significantly smaller radius of curvature in the region in which they are in contact with an inner cylinder surface than half the height of the respective scraper ring.
  • This aspect of the present invention relates in particular only to the upper or lower scraper ring of a three-part oil scraper ring, and not to the height of the entire three-part oil scraper ring.
  • the three-part oil scraper ring is preferably designed such that the expander spring is designed as an MF spring, the upper scraper ring at the pivot point having a curvature that merges smoothly and continuously into the lower flank and forms a tangent to the radius of curvature (R), the Curvature extends over 90 °, so that the expander spring is designed as an MF spring, the upper scraper ring at the pivot point having a curvature that merges smoothly and continuously into the lower flank and forms a tangent to the radius of curvature (R), the Curvature extends over 90 °, so that the
  • Pivot point of the outer ring contour of the tread is formed by the curvature (R), whereby the pivot point is at a distance (R) above the lower flank
  • Curvature (R) then immediately and smoothly changes into a straight section, which in turn merges into an upper radius of curvature (Ro), which is tangential to both the tangential section and the intersection line of the upper flank, the radius (Ro) being smaller is than the radius (R), and where the lower scraper ring is symmetrically spherical in the area of the pivot point, the pivot point is from the lower flank at an axial height between 47 and 53% or approximately 50% of the height H of the lower scraper ring, with the radius R between 0.05 and 0.15mm.
  • the lower scraper ring is symmetrical with respect to a plane that extends along half the height H of the scraper ring.
  • the height H of the lower and / or upper scraper ring is between 0.28 mm and 0.52 mm, preferably between 0.34 mm and 0.46 mm and more preferably between 0.38 and 0.42 mm
  • Exemplary embodiments with a radius of curvature R of the running surface of the lower and / or upper scraper ring between 0.06 mm and 0.04 mm, preferably between 0.08 mm and 0.12 mm and more preferably between 0.09 mm and 0.11 mm are also disclosed .
  • the heights H of the lower and / or upper scraper ring are between 0.28 mm and 0.52 mm and that
  • Radii of curvature R of the treads are between 0.06 mm and 0.04 mm.
  • the height H of the respective scraper ring is between 0.34 mm and 0.46 mm
  • Radius of curvature R of the tread is 0.08mm and 0.12mm.
  • the height H of the respective scraper ring is between 0.38 and 0.42 mm and the radius of curvature R of the tread is between 0.09 mm and 0.1 1 mm.
  • a radially outermost point of the outer ring contour of the tread is at half the height H / 2 of the lower scraper ring.
  • the lower scraper ring is designed so that it touches an inner cylinder surface in the axial direction.
  • the lower wiper ring shows no tendency to twist.
  • Transition between the curvature with the radius of curvature R and the lower flank is provided.
  • the transition here is convex in cross section and merges smoothly and continuously into the curvature R. This should not be stripped oil that has passed the gap between the cylinder inner wall and the tread with the radius R on the tread of the adhering to the upper scraper ring, at the back of the curvature R inward towards the groove base. This works particularly well with the upper wiper ring of a three-part oil wiper ring when the piston moves upwards
  • a transition is provided on the lower scraper ring between the curvature R and the upper flank, the cross section being convex and merging smoothly and smoothly into the curvature R.
  • Transition of the lower scraper ring between the curvature R and the lower flank has a transitional radius of curvature Ru which is between once the height H and 40 times the height H, preferably between twice the height H and 20 times the height H and more preferably between 4 times the height H and 10 times the height H. If the design is symmetrical, this design also affects the transition between the curvature R and the upper flank of the lower scraper ring. In this embodiment there may be a smaller rounding radius between the transition area and the upper flank.
  • a cross section of the lower scraper ring between the curvature R and the lower flank is designed as a spiral curve and preferably as a hyperbolic spiral curve.
  • the spiral curve is preferably convex in cross section and merges smoothly and continuously into the curvature R and into the lower flank surface.
  • Curvature R and the upper flank which then also follows a spiral curve.
  • Oil scraper ring described wherein a radially outermost point of the outer ring contour of the tread of the upper scraper ring is at the level of the upper scraper ring, which the R corresponds to the radius of curvature of the tread, and preferably the radius R of the tread merges smoothly and continuously into the lower flank.
  • the height of the pivot point lies at a height of the upper scraper ring that corresponds to the radius of curvature R, which is why the height value corresponds exactly to the value of the radius of curvature.
  • the upper flank at an outer edge merges smoothly and continuously into the curvature Ro which is smaller than the curvature R of the tread
  • Radii of curvature R and Ro are connected by a common tangent.
  • the two radii of curvature and the tangent together form the outer ring surface of the upper scraper ring.
  • the tangent forms a truncated cone surface, which tapers towards the top of the combustion chamber.
  • Radius of curvature each form part surfaces of gates.
  • the center points of the radii of curvature R and Ro of the upper scraper ring lie on a straight line which is parallel to an axial direction of the upper scraper ring.
  • Pitch circles with the radii R and Ro have an angle of 180 ° in total.
  • the pitch circle with the radius R extends over an angular range of more than 90 °.
  • the pitch circle with the radius R preferably extends over an angular range between 95 ° and 115 °, preferably over an angular range between 98 ° and 110 °, and more preferably over an angular range between 100 ° and 105 °.
  • the pitch circle with the radius Ro extends over an angular range of less than 90 °.
  • the pitch circle with the radius R0 preferably extends over an angular range between 65 ° and 85 °, preferably over an angular range between 70 ° and 82 °, and more preferably over an angular range between 75 ° and 80 °.
  • the tangent distance of the cross section of the upper scraper ring is determined as the root of the sum of the square of the difference between the radii R and Ro and of the square of the difference between the sum of the radii and the height H.
  • the angle of the conical surface which is generated by a rotation of the tangent line about an axial axis of the upper scraper ring, is between 5 ° and 25 °, preferably over an angular range between 8 ° and 20 °, and further preferably over an angular range between 10 ° and 15 °.
  • the upper ring flank of the upper scraper ring merges smoothly and continuously into the curvature Ro in this embodiment, which in turn smoothly and continuously into the
  • Tangent section merges, which in turn merges smoothly and continuously into the curvature R of the tread, which then merges smoothly and continuously into the lower flank.
  • the two radii of curvature and the tangent together form the outer ring surface.
  • the tangent forms a truncated cone surface that tapers towards the top.
  • a radially outermost point of the outer ring contour of the tread is at the height R of the upper one
  • Scraper ring measured from its lower ring flank, and further the transitions between the lower ring flank, the curvature R of the tangent line, the radius of curvature Ro and the upper flank are carried out continuously and smoothly.
  • the radially outer surface is composed of two arcs and a segment, with no edges.
  • the outer ring surface preferably has an axial extent of R, the lower one
  • the shape of the upper scraper ring allows the upper scraper ring to float particularly well on an oil layer when the piston moves upward.
  • an exemplary embodiment of a scraper ring for a three-part oil scraper ring is provided, the radius of curvature having the value R, which is by a factor between 1.5 to 4, preferably between 1.8 to 3 times and more preferably between 2 to 2 , 5 is less than the height H of the scraper ring.
  • This embodiment relates to a scraper ring with a relatively large radius of curvature R.
  • Radius of curvature R of the upper and / or lower scraper ring between 0.03 and 0.2 mm preferably between 0.04 and 0.15 mm and more preferably between 0.05 and 0.10 mm, and a height H of the lower and / or upper scraper ring is between 0.2 and 0.8 mm, preferably between 0.25 and 0, 15mm and more preferably between 0.3 and 0.5mm.
  • Radius of curvature R of the lower and / or upper scraper ring between 0.03 and 0.2 mm, and a height H of the lower and / or upper scraper ring is between 0.2 and 0.8 mm.
  • the radius of curvature R is between 0.04 and 0.15 mm, and a height H of the lower and / or upper scraper ring is between 0.25 and 0.15 mm.
  • the radius of curvature R is between 0.05 and 0.10 mm, and a height H of the lower and / or upper scraper ring is between 0.3 and 0.5 mm.
  • a radially outermost point of the outer ring contour of the tread of the lower scraper ring is between 55 and 80%, preferably between 50 and 75% and more preferably between 65 and 70% of the height H of the lower scraper ring.
  • the lower scraper ring therefore presses against the inner surface of the cylinder, which lies above the center of the lower scraper ring, which causes the lower scraper ring to twist.
  • a lower and an upper transition between the curvature R and the lower flank or the upper flank are provided in the lower scraper ring, which in each case form tangents to the curvature R and which are related to each other extend a radial plane at an angle between 30 ° and 75 ° in the direction of the upper and the lower flank.
  • the transitions are essentially straight, and a corner or edge between the upper or lower transition can also be rounded.
  • the cross-section of the outer ring surface of the lower scraper ring is essentially formed by a circular arc and two tangential sections, which can be referred to as upper or lower transition tangents.
  • the points at which the upper or lower transition in each case merge into the upper or lower flank lie one above the other in the lower and / or upper scraper ring in the axial direction, or have the same radial distance from the axial axis of symmetry.
  • a lower and an upper spiral transition is provided between the radius of curvature R and the lower flank or the upper flank of the lower scraper ring, the spiral transitions in each case smoothly and continuously into the curvature R or the upper / lower Cross flank.
  • This design allows a more even transition between the curvature of the tread and the piston ring flanks than would be possible with straight sections.
  • a spiral transition relates to a cut in the axial direction.
  • a spiral transition is carried out on average as a spiral curve, preferably as a hyperbolic spiral curve.
  • the transitions are convex and preferably merge smoothly into the radius of curvature R and into the flank surfaces.
  • the expander spring is designed as an MF spring.
  • MF expander springs in particular allow particularly good oil passage in the radial direction, since the MF expander spring covers only a small part of the gap between the upper and lower oil control ring compared to the SS50 and MD expander springs.
  • Figure 1 shows a conventional scraper ring in a sectional view.
  • Figure 2 shows a first embodiment of a scraper ring according to the invention in one Sectional view.
  • Figure 3 shows a conventional three-part oil control ring in a sectional view.
  • Figure 4 shows an embodiment of an upper scraper ring according to the invention in a sectional view.
  • Figure 5 shows an embodiment of a lower scraper ring according to the invention in a sectional view.
  • FIG. 6 shows a three-part oil scraper ring with upper and lower scraper rings according to the invention in a sectional view.
  • FIG. 7 shows a three-part oil scraper ring with upper and lower scraper rings according to the invention in a sectional view.
  • FIG. 1 shows a conventional scraper ring 42 in a sectional view.
  • the scraper ring comprises an annular body 4 which is delimited at the top by an upper flank or flank surface 6 and at the bottom by a lower flank surface 8.
  • the outer contour of the ring has a uniform radius of curvature Rsdt.
  • the radius of curvature forms the tread 12 of the scraper ring.
  • the distance between the upper and lower flank surfaces defines the height H of the scraper ring.
  • the uniform radius of curvature Rsdt is exactly half the height H of the scraper ring.
  • the stripping properties of this ring can be influenced by changing the height of the ring, the material and, above all, the radial thickness and the properties of an expander spring used.
  • Scraper rings according to the prior art have a basic semicircular, corresponding outer radius Rsdt, which is directed toward the inner surface of the cylinder and corresponds to half the height H.
  • FIG. 2 shows a first embodiment of a lower scraper ring 26 according to the invention in a sectional view.
  • the lower scraper ring 26 comprises an annular body 4 which is delimited at the top by an upper flank or flank surface 6 and at the bottom by a lower flank surface 8.
  • the height H is also here as the distance between the flank surfaces in Axial direction defined.
  • the ring outer side 12 comprises, in section along the axial direction and through the axial axis of symmetry, an outer ring contour 14.
  • the outer ring contour 14 forms a running surface 16, which has a radius of curvature R which is significantly smaller than the height H.
  • the radius of curvature is by a factor between 3. 5 to 4.5 is less than the height H of the lower scraper ring 26.
  • the curvature with the radius R of the tread 16 goes smoothly and smoothly into the transition 20 between the curvature R and the upper flank and the transition 22 between the curvature R and the lower flank over.
  • the respective radii of curvature of the transitions 20 and 22 can be much larger than the height H. It is also provided that edges that can occur between the transitions 20 and 22 and the flanks 6, 8 are rounded. Overall, the
  • the outer ring surface as a combination of three radii, the radius of curvature R of the tread, which transition above / below into the transitions 20, 22 with the transition radii of curvature Ru.
  • the radially outermost point or pivot point 18 of the outer ring contour of the tread 16 forms the contact point of the outer ring contour 14.
  • the contact point then forms a contact line in the finished lower wiper ring 26.
  • This tread contour is optimized for reduced oil consumption.
  • the area which is to bear against the inner wall of the cylinder has a significantly smaller radius of curvature than in the case of scraper rings of the prior art.
  • the radius of curvature R should be in the range from 0.08 to 0.12mm.
  • the transition areas 20 and 22 are preferably 0.75 mm.
  • the distance r which describes the radial extent of the ring outer surface 12, is between 0.1 to 0.2 mm, and should be 0.15 mm in FIG.
  • the outer contour of the lower scraper ring is mirror-symmetrical with respect to a plane that is halfway through the lower one
  • FIG. 3 shows a conventional three-part oil control ring 44 in a sectional view.
  • the conventional oil scraper ring 44 has a conventional upper scraper ring 42 and a conventional lower scraper ring 42. Both scraper rings are as
  • the stripping process is shown in an upward movement AA. Since the scraper ring is designed symmetrically, the representation of the situation when moving downwards corresponds exactly to that which should occur during an upward movement.
  • the aim is to achieve an improved oil scraper effect and / or a minimum of friction losses compared to a conventional oil scraper ring with identical upper and lower scraper rings.
  • Another important aspect is to avoid or at least to significantly reduce the formation and deposition of oil coal in the area of an expander spring. Furthermore, it is desirable the friction caused by a
  • Oil scraper ring is produced without significant loss in oil consumption.
  • FIG. 4 shows an embodiment of an upper scraper ring according to the invention in a sectional view.
  • the ring of FIG. 4 is not symmetrical with respect to a plane that extends through the piston ring at half the height H.
  • FIG. 4 shows a cross-sectional view through the upper scraper ring 2 with the ring body 4, which is delimited at the top by an upper flank or flank surface 6 and at the bottom by a lower flank surface 8.
  • the ring body is delimited by an inner ring surface 10.
  • the ring inner surface 10 lies opposite the ring outer side 12.
  • the ring outer side 12 forms the outer ring contour 14.
  • the curvature R forms a running surface 16 on the outer ring contour 14.
  • the curvature R merges smoothly and smoothly into the lower flank surface 8, or the lower flank surface forms a tangent to the radius of curvature R.
  • the curvature extends over more than 90 ° so that the radially outermost point or pivot point 18 of the outer ring contour of the running surface 16 is formed by the curvature R.
  • the pivot point 18 is located at a distance R above the lower one
  • the pivot point 18 of the asymmetrically conical rail or upper scraper ring is offset in the direction of the lower flank.
  • the pivot point lies at 20 to 40% of the axial height H of the upper scraper ring.
  • the value of the radius of curvature R thus corresponds to one fifth up to two and a half of the height H.
  • the axial height of the upper scraper ring remains in the range of 0.3 to 0.5 mm.
  • the outer contour of the upper scraper ring is determined by the dimensions of the radius of curvature R and the angle a.
  • the angle a is the
  • the radius will be between 0.15 and 0.25mm and the angle a between 5 and 20 °.
  • the radius Ro can be between 0.1 and 0.2 mm. This scraper ring should be used as an upper scraper ring.
  • FIG. 5 shows a further embodiment of a lower scraper ring according to the invention in a sectional view.
  • a lower scraper ring is provided with a tread 16, which is symmetrically spherical in the area of the pivot point 18.
  • the pivot point is above a central plane H / 2.
  • the pivot point 18 is viewed from the lower flank at an axial height between 55 and 75% of the height H.
  • the radius R that defines the crown of the tread can be in the range between 0.05 and 0.15 mm.
  • the radius of curvature R merges upwards and downwards tangentially into the upper transition tangent 30 and the lower transition tangent 32.
  • Transition tangents can have angles between 30 ° and 75 ° to the axial direction.
  • the transition tangents 30 and 32 merge into the upper or lower flank, which can be rounded.
  • Scraper ring can be expected to reduce friction.
  • FIG. 6 shows a three-part oil scraper ring with scraper rings according to the invention in a sectional view.
  • the three-part oil scraper ring comprises an upper scraper ring 24 which is designed in accordance with the embodiment in FIG.
  • the three-part oil scraper ring comprises a lower scraper ring 23 which is designed in accordance with the embodiment in FIG.
  • This oil scraper ring according to the invention uses for the first time two different scraper rings with two different scraper ring contours in one oil scraper ring.
  • the upper scraper ring 24 and the lower scraper ring 26 are pressed radially outward against an inner cylinder surface 38 by an expander spring 34 which is designed as an MF meander spring.
  • the MF meander spring 34 maintains a defined axial distance between the upper scraper ring 24 and the lower scraper ring 26.
  • the oil scraper ring moves upwards in the axial direction, as indicated by arrow AA.
  • the upper scraper ring 24 Due to the partially conical tread 16, the upper scraper ring 24 produces an “oil catching effect” in which the upper scraper ring 24 floats on the oil and the oil gets between the scraper rings 24, 26.
  • the upper scraper 24 can prevent the oil from jamming in front of the upper scraper ring 24 and the conical part collects above between the upper scraper ring flank 6 and an upper piston ring groove flank.
  • the lower scraper ring 26 arranged at the bottom with a symmetrically spherical running surface prevents the oil O from leaving the annular space downwards.
  • a likewise conical lower scraper ring would result in too much oil collecting between an outer piston surface and the inner cylinder surface 38 and being able to cause increased friction.
  • FIG. 7 shows a three-part oil scraper ring from FIG. 6 during a movement in
  • the upper scraper ring 24 creates a thin oil film due to the partially conical tread 16, since the upper scraper ring 24 does not float on the oil film due to the missing slope and pushes the oil O in front of it for the most part. Due to its smaller radius of curvature R, the upper scraper ring 24 has a greater scraper power than the lower scraper ring 26. The difference in the scraper powers is derived between the upper scraper ring 24 and the lower scraper ring 26 in the direction of the groove base (not shown).
  • an upper scraper ring 24 with an asymmetrically conical outer surface is used, while a lower scraper ring 26 with a symmetrically crowned running surface is used.
  • the lubricating oil is collected on the cylinder running surface in the upward stroke and collected by the “oil catching effect” between the upper scraper ring 24 and the lower scraper ring 26 and discharged in the direction of the piston ring groove base.
  • the stripped oil can get back into the crankcase through appropriate channels in the piston.
  • the principle is based on an asymmetrical wiping performance of the upper wiper ring 24, the
  • Wiping performance during a downward movement is above that of the lower wiper ring 26. This is achieved in that the curvature of the tread at the upper scraper ring 24 is smaller than the curvature of the tread at the lower scraper ring 26. With this, stripped oil collects between the scraper rings 24 and 26 during a downward movement of the upper scraper ring 24 a floating of the upper scraper ring 24 on the oil layer, which significantly reduces the scraper performance. The wiping performance of the upper wiper ring 24 becomes preferably reduced below that of the lower scraper ring 26. This means that even when moving upwards, more oil is wiped off the “rear” wiper ring in the direction of movement. Overall, both with an upward movement AA and with a downward movement, oil is caught between the scraper rings 24, 26 and transported in the direction of the groove base and further into the crankcase.
  • a scraper ring according to FIG. 2 can also be used.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)

Abstract

L'invention concerne un segment racleur d'huile en trois parties, comprenant un segment racleur supérieur (24) et un segment racleur inférieur (26). Les segments racleurs (24, 26) sont maintenus espacés par un ressort expanseur (34) et sont poussés dans le sens radial vers l'extérieur. Le segment racleur supérieur (24) comporte un corps annulaire (4) pourvu d'un flanc supérieur (6), d'un flanc inférieur (8), d'une surface intérieure de segment (10) et d'une surface extérieure de segment (12) qui, en coupe dans le sens axial (A), présente un contour extérieur de segment (14). Le corps annulaire (4) présente une hauteur H qui, vue dans le sens axial (A), correspond à l'écart le plus grand entre le flanc supérieur (6) et le flanc inférieur (8). Le contour extérieur de segment (14) forme une surface de roulement (16) qui présente un rayon de courbure R qui est inférieur à la hauteur H du segment racleur supérieur (24) d'un facteur compris entre 1,5 et 6.
PCT/EP2019/063852 2018-08-13 2019-05-28 Segment racleur d'huile en trois parties WO2020035188A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
US17/268,140 US11719340B2 (en) 2018-08-13 2019-05-28 Three-part oil scraper ring
CN201980053118.1A CN112654807B (zh) 2018-08-13 2019-05-28 三组件刮油环
EP19727387.3A EP3797233B1 (fr) 2018-08-13 2019-05-28 Segment racleur d'huile en trois parties

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE102018119584.2 2018-08-13
DE102018119584 2018-08-13
DE102018120962.2 2018-08-28
DE102018120962.2A DE102018120962A1 (de) 2018-08-13 2018-08-28 Dreiteiliger Ölabstreifring

Publications (1)

Publication Number Publication Date
WO2020035188A1 true WO2020035188A1 (fr) 2020-02-20

Family

ID=66676546

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2019/063852 WO2020035188A1 (fr) 2018-08-13 2019-05-28 Segment racleur d'huile en trois parties

Country Status (6)

Country Link
US (1) US11719340B2 (fr)
EP (1) EP3797233B1 (fr)
CN (1) CN112654807B (fr)
DE (1) DE102018120962A1 (fr)
PT (1) PT3797233T (fr)
WO (1) WO2020035188A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN116897254A (zh) * 2021-03-31 2023-10-17 株式会社理研 侧轨及具备该侧轨的控油环

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5962358U (ja) * 1982-10-16 1984-04-24 株式会社リケン 組合せリング
DE3833322A1 (de) * 1988-05-26 1989-12-07 Cofap Kolbenring fuer innenverbrennungsmotoren
JPH08159282A (ja) 1994-12-05 1996-06-21 Riken Corp 内燃機関用オイルコントロールリング
US20160076649A1 (en) 2014-09-12 2016-03-17 Mazda Motor Corporation Oil ring
DE112015001071T5 (de) 2014-03-01 2016-12-08 Mahle International Gmbh Ölabstreifringanordnung
US20170184198A1 (en) 2015-12-25 2017-06-29 Honda Motor Co., Ltd. Oil ring
DE102016104853A1 (de) * 2016-03-16 2017-09-21 Federal-Mogul Burscheid Gmbh Mehrteiliger Ölabstreif-Kolbenring mit verringerter Reibung
EP3270012A1 (fr) 2015-03-12 2018-01-17 Kabushiki Kaisha Riken Rail latéral

Family Cites Families (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2397220A (en) * 1941-04-17 1946-03-26 Perfect Circle Co Piston ring
US2424881A (en) * 1944-09-30 1947-07-29 Albert P Fall Piston ring assembly
US2712971A (en) * 1952-05-17 1955-07-12 Hastings Mfg Co Piston ring assembly and elements thereof
US3325883A (en) * 1962-11-26 1967-06-20 Dana Corp Method of making a piston ring assembly
FR2436160A1 (fr) * 1978-09-13 1980-04-11 Cib Composition bitumineuse contenant des polymeres et ses applications
JP4203365B2 (ja) * 2003-06-20 2008-12-24 帝国ピストンリング株式会社 ピストンリング
DE10340302A1 (de) * 2003-09-02 2005-04-14 Mahle Gmbh Ölabstreifring für Kolben von Verbrennungsmotoren
JP2007077988A (ja) * 2005-09-13 2007-03-29 Waertsilae Schweiz Ag ピストンリング一式
DE102007027815A1 (de) * 2007-06-13 2008-12-24 Federal-Mogul Burscheid Gmbh Ölabstreifring
DE102009036240B4 (de) * 2009-08-05 2014-11-13 Federal-Mogul Burscheid Gmbh Kompressionskolbenring
DE102012000241B4 (de) * 2011-05-10 2016-12-08 Federal-Mogul Burscheid Gmbh Kolbenring für 2-Taktmotoren
DE102012010756B4 (de) * 2012-05-31 2017-04-27 Federal-Mogul Burscheid Gmbh Verfahren zur Herstellung eines Ölabstreifkolbenrings
US20180274675A1 (en) * 2012-11-09 2018-09-27 Federal-Mogul Burscheid Gmbh Piston ring with varying apex lines
WO2015101938A1 (fr) * 2013-12-30 2015-07-09 Mahle International Gmbh Ensemble segment racleur d'huile
WO2015199183A1 (fr) * 2014-06-27 2015-12-30 株式会社リケン Segment de piston
US20160040622A1 (en) * 2014-08-05 2016-02-11 General Electric Company Piston assembly for a reciprocating engine
JP5833276B1 (ja) * 2014-09-12 2015-12-16 Ｔｐｒ株式会社 組合せオイルリング
CN204783306U (zh) * 2015-06-02 2015-11-18 潍柴动力股份有限公司 新型活塞结构
DE102016110131A1 (de) * 2016-06-01 2017-12-07 Federal-Mogul Burscheid Gmbh Zweiteiliger Ölabstreifring mit Öldruckeffektstegen
WO2019008780A1 (fr) * 2017-07-05 2019-01-10 Ｔｐｒ株式会社 Bague de graissage combinée
DE102018119586A1 (de) * 2018-08-13 2020-02-13 Federal-Mogul Burscheid Gmbh Abstreifring für einen dreiteiligen Ölabstreifring und dreiteiliger Ölabstreifring

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5962358U (ja) * 1982-10-16 1984-04-24 株式会社リケン 組合せリング
DE3833322A1 (de) * 1988-05-26 1989-12-07 Cofap Kolbenring fuer innenverbrennungsmotoren
JPH08159282A (ja) 1994-12-05 1996-06-21 Riken Corp 内燃機関用オイルコントロールリング
DE112015001071T5 (de) 2014-03-01 2016-12-08 Mahle International Gmbh Ölabstreifringanordnung
US20160076649A1 (en) 2014-09-12 2016-03-17 Mazda Motor Corporation Oil ring
EP3270012A1 (fr) 2015-03-12 2018-01-17 Kabushiki Kaisha Riken Rail latéral
US20170184198A1 (en) 2015-12-25 2017-06-29 Honda Motor Co., Ltd. Oil ring
DE102016104853A1 (de) * 2016-03-16 2017-09-21 Federal-Mogul Burscheid Gmbh Mehrteiliger Ölabstreif-Kolbenring mit verringerter Reibung

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN116897254A (zh) * 2021-03-31 2023-10-17 株式会社理研 侧轨及具备该侧轨的控油环
US11994219B2 (en) 2021-03-31 2024-05-28 Kabushiki Kaisha Riken Side rail and oil control ring comprising same

Also Published As

Publication number Publication date
CN112654807B (zh) 2023-02-21
DE102018120962A1 (de) 2020-02-13
PT3797233T (pt) 2022-10-21
US11719340B2 (en) 2023-08-08
EP3797233B1 (fr) 2022-09-28
CN112654807A (zh) 2021-04-13
EP3797233A1 (fr) 2021-03-31
US20210332885A1 (en) 2021-10-28

Similar Documents

Publication Publication Date Title
EP3797234B1 (fr) Segment racleur pour un segment racleur d'huile en trois parties et segment racleur d'huile en trois parties
EP2855981B1 (fr) Procédé de production d'un segment de piston racleur d'huile
DE19651112C5 (de) Dichtungsvorrichtung für eine Motorkolbenstange
EP2162648B1 (fr) Segment de piston pour le piston d'un moteur a combustion interne
EP3797233B1 (fr) Segment racleur d'huile en trois parties
WO2018172144A1 (fr) Chemise de cylindre
EP3636967B1 (fr) Anneau déflecteur d'huile pour une tige de piston
DE102017100173A1 (de) Kolbenring mit gestufter Lauffläche
EP3325855B1 (fr) Segment de piston
WO2017174706A1 (fr) Dispositif de séparation des gouttelettes d'huile et/ou du brouillard d'huile
DE102017215834A1 (de) Kolben
EP3036460B1 (fr) Segment de piston
EP3717804B1 (fr) Bague de piston et combinaison de bague de piston et de piston à propriétés d'usure améliorées
DE102017107009B4 (de) Spielfreier Ölabstreifring
DE102014209577A1 (de) Kolbenring mit innenseitiger Profilierung in Umfangsrichtung
DE102020100760B4 (de) Kompressions-Kolbenring mit verbesserter Ölrückhaltewirkung
DE102019110583B4 (de) Zweiteiliger Ölabstreifring mit vorteilhafter Geometrie
EP3850249B1 (fr) Segment de piston et piston à scellement intérieur de rainure
EP4136370B1 (fr) Segment racleur d'huile destiné à des pistons d'un moteur à combustion interne
DE102017200510A1 (de) Flachdichtung mit Haftungsoptimierung
EP2639004B1 (fr) Segment de couronne d'aubes avec surface de limitation de l'espace annulaire à profil en hauteur ondulé et procédé de fabrication
DE202009013834U1 (de) Ölabstreifring
DE102016101010B3 (de) Verdrehter Kolbenring
DE102018201881A1 (de) Kolben für einen Verbrennungsmotor und Verfahren zur Herstellung eines Kolbens
DE102008047268A1 (de) Käfig für ein Lager, insbesondere für ein Wälzlager

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 19727387

Country of ref document: EP

Kind code of ref document: A1

ENP Entry into the national phase

Ref document number: 2019727387

Country of ref document: EP

Effective date: 20201222